TWI821920B - Combination of hydrodynamic bearing and wing plate - Google Patents

Abstract

A combination of a hydrodynamic bearing and a wing plate includes the hydrodynamic bearing, a rotating shaft and the wing plate. The rotating shaft is disposed on the wing plate, and is inserted into a shaft hole of the hydrodynamic bearing. An inner wall of the shaft hole of the hydrodynamic bearing is provided with at least two oil-guiding groove sets, each oil-guiding groove set includes a plurality of oil-guiding grooves, and a cusps is formed at the bend of each oil-guiding groove. The cusps of the oil-guiding grooves of the same oil-guiding groove set forms a corresponding cusp point arranged along the circumferential direction in the shaft hole. An active area is formed between the corresponding cusps of each adjacent two oil-guiding groove sets in the shaft hole, and a mass center of the wing plate and the rotating shaft is in or close to the active area. Therefore, the hydrodynamic bearing has better supporting force that can support the balanced rotation of the rotating shaft and the wing plate, and effectively reduces the generation of noise and vibration.

Description

Hydrodynamic bearing and its combination with wing plate

The present invention relates to a hydrodynamic bearing, and in particular to a hydrodynamic bearing that can pass fluid between a bearing and a rotating shaft and generate a pressure field due to changes in flow speed, so that the rotating shaft can rotate stably without contacting the bearing and its combination with Wing panel combination.

Existing hydrodynamic bearings are equipped with oil guide grooves on the inner wall of the bearing body or the outer wall of the rotating shaft. When the lubricating fluid flows between the rotating shaft and the bearing body, it can form a concentrated pressure, which uses the support force of the oil film to rotate the rotating shaft. It will not come into contact with the shaft hole, so it can avoid the collision and wear of the shaft and the bearing body, thereby reducing noise and vibration. It has become a commonly used bearing technology in today's information products. The hydrodynamic bearing can be installed on the wing plate of the fan to support the rotation of the fan wing. However, the hydrodynamic bearing cannot provide better support force for the rotating shaft and the wing plate, so there will still be a gap between the rotating shaft and the hydrodynamic bearing. Collision, resulting in noise and vibration.

The technical problem to be solved by the present invention is to provide a hydrodynamic pressure bearing and its combination with the wing plate in view of the shortcomings of the existing technology. The hydrodynamic pressure shaft can provide better support force for the rotating shaft and the wing plate, so that the rotating shaft and the hydrodynamic pressure shaft can be There will be no collision between the bearings, which can effectively avoid noise and vibration.

In order to solve the above technical problems, the present invention provides a hydrodynamic bearing that can be combined with a rotating shaft and a wing plate. One end of the rotating shaft is fixed to the wing plate. The hydrodynamic bearing has a bearing body, and the inside of the bearing body A rotating shaft hole is formed, and the inner wall of the rotating shaft hole is provided with at least two oil-conducting groove groups. Each of the oil-conducting groove groups includes a plurality of oil-conducting grooves, and these oil-conducting grooves are bent in a V-shape. The rotating shaft can be inserted into the rotating shaft hole, and a gap is formed between the rotating shaft and the hydrodynamic bearing to accommodate lubricating fluid; a sharp point is formed at the bend of each oil guide groove, and the same The sharp points of the plurality of oil guide grooves of the oil guide groove group form a sharp point corresponding to the circumferential direction in the rotating shaft hole, and each of the two adjacent oil guide groove groups in the rotating shaft hole An active area area is formed between the corresponding points of the cusps. The center of mass of the wing plate and the rotating shaft lies within or close to the active area area. The center of mass of the wing plate and the rotating shaft is close to the active area area. , means that the active area area forms an active area length along the axial direction of the hydrodynamic bearing, the center of mass of the wing plate and the rotating shaft is outside the active area area, and the distance from the active area area is Within one-tenth of the area length.

Preferably, the outer diameter of the wing plate is defined as a wing diameter, the wing plate has a first end surface, the hydrodynamic pressure bearing can be installed in a shell cover, the shell cover has a second end surface, and the first end surface And the second end surface is located on the side of the wing plate and the shell cover that are far away from each other. The distance between the first end surface and the second end surface is defined as a fan height. The height of the fluid dynamic pressure bearing is defined as a bearing height. The fluid The inner diameter of the dynamic pressure bearing is defined as the inner diameter of the bearing, the height of the bearing is 0.6mm to 15mm, the inner diameter of the bearing is 0.6mm to 5mm, the height of the fan is 1mm to 150mm, and the size of the wing diameter is 1mm to 150mm.

In order to solve the above technical problems, the present invention provides a combination of a fluid dynamic pressure bearing and a wing plate, which includes: a rotating shaft; a wing plate, one end of the rotating shaft is fixed to the wing plate; and a hydrodynamic pressure bearing, the hydrodynamic pressure shaft The bearing has a bearing body, and a rotating shaft hole is formed in the bearing body. The inner wall of the rotating shaft hole is provided with at least two oil-conducting groove groups. Each of the oil-conducting groove groups includes a plurality of oil-conducting grooves. The oil guide groove is bent in a V shape, and the rotating shaft is inserted into the rotating shaft hole. A gap is formed between the rotating shaft and the hydrodynamic bearing to accommodate lubricating fluid; the curve of each oil guide groove is A sharp point is formed at the fold, and the sharp points of the plurality of oil guide grooves of the same oil guide groove group form a corresponding point corresponding to the sharp point arranged along the circumferential direction in the rotating shaft hole. An active area is formed between the corresponding points of each adjacent two oil-conducting groove groups. The center of mass of the wing plate and the rotating shaft falls within or is close to the active area area. The wing plate and the rotating shaft are located in the active area area. The center of mass of the rotating shaft is close to the active area area, which means that the active area area forms an active area length along the axial direction of the hydrodynamic bearing, the center of mass of the wing plate and the rotating shaft is outside the active area area, and The distance from the active area is within one-tenth of the length of the active area.

The beneficial effect of the present invention is that the hydrodynamic bearing provided by the present invention can be used in combination with a rotating shaft and a wing plate. The inner wall of the rotating shaft hole of the hydrodynamic bearing is provided with at least two oil-conducting groove groups. The oil guide groove group includes multiple oil guide grooves, and a sharp point is formed at the bend of each oil guide groove. The sharp points of multiple oil guide grooves in the same oil guide groove group form a point in the rotating shaft hole. The corresponding points of the sharp points arranged along the circumferential direction form an active area area between the corresponding points of the sharp points of each adjacent two oil guide groove groups in the rotating shaft hole. The center of mass of the wing plate and the rotating shaft falls in the active area area. Within or close to the active area, the hydrodynamic bearing has better support strength and can support the balanced rotation of the rotating shaft and wing plates, effectively preventing the rotating shaft and the bearing body from colliding with each other and causing wear, thereby reducing noise and vibration. , and the service life is increased.

In order to further understand the features and technical content of the present invention, please refer to the following detailed description and drawings of the present invention. However, the drawings provided are only for reference and illustration and are not used to limit the present invention.

The following is a description of the relevant implementation modes disclosed in the present invention through specific specific examples. Those skilled in the art can understand the advantages and effects of the present invention from the content disclosed in this specification. The present invention can be implemented or applied through other different specific embodiments, and various details in this specification can also be modified and changed based on different viewpoints and applications without departing from the concept of the present invention. In addition, the drawings of the present invention are only simple schematic illustrations and are not depictions based on actual dimensions, as is stated in advance. The following embodiments will further describe the relevant technical content of the present invention in detail, but the disclosed content is not intended to limit the scope of the present invention. In addition, the term "or" used in this article shall include any one or combination of more of the associated listed items depending on the actual situation.

[Example]

Referring to Figures 1 to 3, the present invention provides a hydrodynamic bearing. The hydrodynamic bearing 1 can be combined with a rotating shaft 2 and a wing plate 3. The wing plate 3 is a wing plate of a fan. The rotating shaft 2 is disposed on On the wing plate 3, the rotating shaft 2 is a cylindrical shaft body, and one end of the rotating shaft 2 is fixed on the wing plate 3, so that the rotating shaft 2 is arranged upright on the wing plate 3. The hydrodynamic bearing 1 can be installed in a shell cover 4, the rotating shaft 2 is matched with the hydrodynamic bearing 1, and the hydrodynamic bearing 1 can support the rotation of the rotating shaft 2 and the wing plate 3. A wear-resistant piece 5 can also be disposed in the shell cover 4, and the other end of the rotating shaft 2 resists the wear-resistant piece 5, thereby reducing the frictional resistance of the rotating shaft 2.

The hydrodynamic bearing 1 is made of solid material by turning. The hydrodynamic bearing 1 has a bearing body 11. The bearing body 11 is in the form of a hollow cylinder. The outer wall (outer surface) of the bearing body 11 can be of equal diameter. Or with unequal diameters, a rotating shaft hole 12 is formed in the bearing body 11 . The rotating shaft hole 12 is a round hole. The rotating shaft hole 12 can penetrate to both ends of the bearing body 11 , and the rotating shaft hole 12 can cooperate with the rotating shaft 2 . The inner wall (inner surface) of the shaft hole 12 is provided with at least two oil-conducting groove groups 13. The oil-conducting groove groups 13 can be provided with two, three, or four groups, and their number is not limited. Each oil guide groove group 13 includes a plurality of oil guide grooves 131. The oil guide grooves 131 are bent in a V-shape, that is, in a herringbone shape. The oil guide grooves 131 can be arranged at equal intervals. settings. The rotating shaft 2 is inserted into the rotating shaft hole 12, and the oil guide grooves 131 can be used to guide the lubricating fluid, so that the lubricating fluid flows between the rotating shaft 2 and the bearing body 11, and concentrates to form a pressure, with the support force of the oil film. , so that the rotating shaft 2 will not contact the inner wall of the rotating shaft hole 12 when rotating, which can prevent the rotating shaft 2 and the bearing body 11 from colliding with each other and causing wear, thereby reducing noise and vibration.

The present invention can use the gap between the rotating shaft 2 and the hydrodynamic bearing 1 to accommodate lubricating fluid, which can be selected from different types of oils (including ester oils, fluorine oils, and silicone oils), and matched with The herringbone-shaped oil guide groove 131 is designed to achieve non-contact and stable operation of the hydrodynamic bearing 1 and the rotating shaft 2 under different regional environmental conditions. Preferably, the gap G between the rotating shaft 2 and the fluid dynamic pressure bearing 1 is 1 μm to 10 μm. The gap G between the rotating shaft 2 and the fluid dynamic pressure bearing 1 can be 1 μm, 2 μm, 3 μm, 4 μm, 5 μm, 6 μm, 7 μm, 8 μm, 9 μ or 10 μm, etc., to form an optimized gap with better supporting force, so that there will be no collision between the rotating shaft 2 and the hydrodynamic bearing 1, and the generation of noise and vibration can be effectively avoided.

The different regional environments include, for example, polar climate, temperate climate, tropical climate, etc., and correspondingly choose different types of oil products (lubricating fluids). The oil loss rate is less than 10%, and the oil loss rate is preferably 3%. to 4%. The viscosity of ester oils easily changes with the ambient temperature, and the applicable temperature range is -40°C to 150°C. For example, it can be used in the equator, North Asia and other regions, and can be used in electronic products, etc. The viscosity of fluorocarbon oils changes little with the ambient temperature, and is relatively stable at high and low temperatures. The viscosity does not change much. The applicable temperature range is -50°C to 250°C. For example, it can be used in North Asia, South Asia and other regions. In areas with extremely high and extremely low temperatures, it can be used in electronics, automotive products, etc. The viscosity of silicone oil changes little with the ambient temperature, and its applicable temperature range is -50°C to 160°C. For example, it can be used in polar regions and other electronic and automotive products. The present invention can be applied to miniaturized, high-speed products, such as 3C products, cooling components of automobiles (such as electric vehicles), instrument panels, cooling components of drones, e-sports mobile phones, game consoles, projectors, and notebook computers. and servers, etc.

The outer diameter of the wing plate 3 can be defined as a wing diameter A. The wing plate 3 has a first end surface 31. The shell cover 4 has a second end surface 41. The first end surface 31 and the second end surface 41 are located between the wing plate 3 and the second end surface 41. On the side of the shell cover 4 that is far away from each other, the distance between the first end surface 31 and the second end surface 41 can be defined as a fan height B, and the fan height B can also be regarded as the overall height of the fan. The height of the hydrodynamic bearing 1 can be defined as a bearing height C. The bearing height C is the length of the hydrodynamic bearing 1 along the axial direction. The inner diameter of the hydrodynamic bearing 1 can be defined as a bearing inner diameter D. , the inner diameter D of the bearing is the inner diameter of the rotating shaft hole 12 .

The bearing height C and bearing inner diameter D can be adjusted according to the fan height B and wing diameter A. The bearing height C is 0.6mm to 15mm, and the bearing height C can be 0.6mm, 0.7mm, 0.8mm, 0.9mm, 1mm, 2mm, 3mm, 4mm, 5mm, 7mm, 9mm, 10mm or 15mm, etc. The inner diameter D of the bearing is 0.6mm to 5mm, and the inner diameter D of the bearing can be 0.6mm, 0.7mm, 0.8mm, 0.9mm, 1mm, 2mm, 3mm, 4mm or 5mm, etc. This embodiment has better supporting strength and can effectively avoid the generation of noise and vibration.

The height B of the fan is 1mm to 150mm. The height B of the fan can be 1mm, 2mm, 3mm, 4mm, 5mm, 7mm, 9mm, 10mm, 15mm, 20mm, 30mm, 40mm, 50mm, 60mm, 70mm, 80mm, 90mm, 100mm , 110mm, 120mm, 130mm, 140mm or 150mm, etc. The size of the wing diameter A is 1mm to 150mm. The size of the wing diameter A can be 1mm, 2mm, 3mm, 4mm, 5mm, 7mm, 9mm, 10mm, 15mm, 20mm, 30mm, 40mm, 50mm, 60mm, 70mm, 80mm. , 90mm, 100mm, 110mm, 120mm, 130mm, 140mm or 150mm, etc. The size of the fan height B and wing diameter A can be adjusted according to market trends. This embodiment has better supporting strength and can effectively avoid the generation of noise and vibration.

In this embodiment, when the inner diameter D of the bearing is 0.6mm to 2mm, and the height C of the bearing is 0.6mm to 2mm, the included angle θ of the oil guide groove 131 is 10 degrees to 40 degrees. The angle θ of 131 can be 10 degrees, 15 degrees, 20 degrees, 25 degrees, 30 degrees, 35 degrees or 40 degrees, etc. When the inner diameter D of the bearing is 2 mm to 5 mm, and the height C of the bearing is 2 mm to 15 mm, the included angle θ of the oil guide groove 131 is 30 degrees to 90 degrees, and the included angle θ of the oil guide groove 131 can be 30 degrees. , 35 degrees, 40 degrees, 45 degrees, 50 degrees, 55 degrees, 60 degrees, 65 degrees, 70 degrees, 75 degrees, 80 degrees, 85 degrees or 90 degrees, etc. This embodiment has better supporting strength and can effectively avoid the generation of noise and vibration.

The positions of the oil guide grooves 131 can be adjusted according to the force the fan system withstands and the design parameters can be adjusted. A sharp point 132 is formed at the bend of each oil guide groove 131. The sharp points 132 of the multiple oil guide grooves 131 of the same oil guide groove group 13 are located at the same horizontal height, that is, the same oil guide groove. The sharp points 132 of the plurality of oil guide grooves 131 of the groove group 13 form a sharp point corresponding point 121 arranged along the circumferential direction in the rotating shaft hole 12. The plurality of oil guide grooves 131 of each oil guide groove group 13 The sharp points 132 of the oil grooves 131 are formed with sharp point corresponding points 121 arranged along the circumferential direction in the rotating shaft hole 12, and the sharp point corresponding points 121 of each two adjacent oil guide groove groups 13 in the rotating shaft hole 12 are formed. An active area area E is formed between them. The center of mass F of the wing plate 3 and the rotating shaft 2 falls within the active area area E or is close to the active area area E, so that the hydrodynamic pressure axis 1 can provide better contact between the rotating shaft 2 and the wing plate 3. Support strength. In this embodiment, the center of mass F of the wing plate 3 and the rotating shaft 2 falls within the active area area E.

The mass center F of the wing plate 3 and the rotating shaft 2 is close to the active area area E, which means that the active area area E forms an active area length H along the axial direction of the hydrodynamic bearing 1. The mass center F of the wing plate 3 and the rotating shaft 2 F is outside the active area area E, and the distance from the active area area E is within one-tenth of the active area length H. In this way, even if the mass center F of the wing plate 3 and the rotating shaft 2 does not fall within the active area area E Within, but still close to the active area area E, the hydrodynamic pressure shaft 1 can also provide better support force for the rotating shaft 2 and the wing plate 3.

[Beneficial effects of the embodiment]

The beneficial effect of the present invention is that the hydrodynamic bearing provided by the present invention can be used in combination with a rotating shaft and a wing plate. The inner wall of the rotating shaft hole of the hydrodynamic bearing is provided with at least two oil-conducting groove groups. The oil guide groove group includes multiple oil guide grooves, and a sharp point is formed at the bend of each oil guide groove. The sharp points of multiple oil guide grooves in the same oil guide groove group form a point in the rotating shaft hole. The corresponding points of the sharp points arranged along the circumferential direction form an active area area between the corresponding points of the sharp points of each adjacent two oil guide groove groups in the rotating shaft hole. The center of mass of the wing plate and the rotating shaft falls in the active area area. Within or close to the active area, the hydrodynamic bearing has better support strength and can support the balanced rotation of the rotating shaft and wing plates, effectively preventing the rotating shaft and the bearing body from colliding with each other and causing wear, thereby reducing noise and vibration. , and the service life is increased.

The contents disclosed above are only preferred and feasible embodiments of the present invention, and do not limit the scope of the patent application of the present invention. Therefore, all equivalent technical changes made by using the description and drawings of the present invention are included in the application of the present invention. within the scope of the patent.

1:Fluid dynamic pressure bearing 11:Bearing body 12:Rotation shaft hole 121:Corresponding point of sharp point 13: Oil guide groove group 131:Oil guide groove 132: sharp point 2:Rotating shaft 3: Wing plate 31: First end face 4: Shell cover 41:Second end face 5: Wear-resistant sheet A:wing diameter B:Fan height C: Bearing height D: Bearing inner diameter E:Action area F: center of mass of wing plate and rotating shaft G: The gap between the rotating shaft and the hydrodynamic bearing H: length of action area θ: Angle of oil guide groove

Figure 1 is a cross-sectional view of the combination of a hydrodynamic bearing and a wing plate according to the present invention.

Figure 2 is a cross-sectional view of the fluid dynamic bearing of the present invention.

Figure 3 is a perspective view of the hydrodynamic bearing of the present invention.

1:Fluid dynamic pressure bearing 11:Bearing body 12:Rotation shaft hole 121:Corresponding point of sharp point 2:Rotating shaft 3: Wing plate 31: First end face 4: Shell cover 41:Second end face 5: Wear-resistant sheet A:wing diameter B:Fan height C: Bearing height D: Bearing inner diameter E:Action area F: center of mass of wing plate and rotating shaft G: The gap between the rotating shaft and the hydrodynamic bearing H: length of action area

Claims (12)

A hydrodynamic bearing that can be combined with a rotating shaft and a wing plate. The wing plate is a wing plate of a fan. One end of the rotating shaft is fixed to the wing plate. The hydrodynamic pressure bearing has a bearing body formed in the bearing body. There is a rotating shaft hole, and the inner wall of the rotating shaft hole is provided with at least two oil-conducting groove groups. Each of the oil-conducting groove groups includes a plurality of oil-conducting grooves. The oil-conducting grooves are bent in a V-shape. The rotating shaft can be inserted into the rotating shaft hole, and a gap is formed between the rotating shaft and the hydrodynamic bearing to accommodate lubricating fluid; a sharp point is formed at the bend of each oil guide groove, and the same as the oil guide groove. The sharp points of the plurality of oil guide grooves of the oil groove group form a sharp point corresponding to the circumferential direction in the rotating shaft hole. An active area area is formed between the corresponding points of the cusp points. The center of mass of the wing plate and the rotating shaft lies within or close to the active area area. The center of mass of the wing plate and the rotating shaft is close to the active area area. It means that the active area area forms an active area length along the axial direction of the hydrodynamic bearing, the center of mass of the wing plate and the rotating shaft is outside the active area area, and the distance from the active area area is the active area area Within one tenth of the length. The fluid dynamic pressure bearing of claim 1, wherein the outer diameter of the wing plate is defined as a wing diameter, the wing plate has a first end surface, and the hydrodynamic pressure bearing can be installed in a shell cover, the shell cover has A second end surface, the first end surface and the second end surface are located on the side of the wing plate and the shell cover that are far away from each other. The distance between the first end surface and the second end surface is defined as a fan height. The fluid dynamic pressure bearing The height is defined as a bearing height, the inner diameter of the hydrodynamic bearing is defined as a bearing inner diameter, the bearing height is 0.6mm to 15mm, the bearing inner diameter is 0.6mm to 5mm, the fan height is 1mm to 150mm, the The size of the wing diameter ranges from 1mm to 150mm. The hydrodynamic bearing as described in claim 2, wherein the inner diameter of the bearing is 0.6mm to 2mm, the height of the bearing is 0.6mm to 2mm, and the included angle of each oil guide groove is 10 degrees to 40 degrees. The fluid dynamic pressure bearing according to claim 2, wherein the inner diameter of the bearing is 2 mm to 5 mm, the height of the bearing is 2 mm to 15 mm, and the included angle of each oil guide groove is 30 degrees to 90 degrees. The fluid dynamic pressure bearing according to claim 1, wherein the gap between the rotating shaft and the fluid dynamic pressure bearing is 1 μm to 10 μm. The fluid dynamic pressure bearing as described in claim 1, wherein the applicable temperature range of the fluid dynamic pressure bearing is -40°C to 150°C, the lubricating fluid is ester oil, or the applicable temperature range of the fluid dynamic pressure bearing is -50℃ to 250℃, the lubricating fluid is fluorine oil, or the applicable temperature range of the hydrodynamic bearing is -50℃ to 160℃, the lubricating fluid is silicone oil. A combination of a fluid dynamic pressure bearing and a wing plate, including: a rotating shaft; a wing plate, which is a wing plate of a fan, and one end of the rotating shaft is fixed to the wing plate; and a hydrodynamic pressure bearing, the fluid dynamic pressure bearing It has a bearing body, a rotating shaft hole is formed in the bearing body, and the inner wall of the rotating shaft hole is provided with at least two oil-conducting groove groups. Each of the oil-conducting groove groups includes a plurality of oil-conducting grooves. The oil groove is bent in a V shape, and the rotating shaft is inserted into the rotating shaft hole. A gap is formed between the rotating shaft and the hydrodynamic bearing to accommodate lubricating fluid; wherein the bending of each oil guide groove is A sharp point is formed at the same oil guide groove group, and the sharp points of the multiple oil guide grooves of the same oil guide groove group form a corresponding point corresponding to the sharp point arranged along the circumferential direction in the rotating shaft hole. An active area is formed between the corresponding points of the adjacent two oil-conducting groove groups. The center of mass of the wing plate and the rotating shaft falls within or is close to the active area area. The wing plate and the rotating shaft are located in the active area area. The center of mass of the rotating shaft is close to the active area Domain means that the active area area forms an active area length along the axial direction of the hydrodynamic bearing. The center of mass of the wing plate and the rotating shaft is outside the active area area, and the distance from the active area area is Within one tenth of the length of the active area. The combination of a hydrodynamic bearing and a wing plate as described in claim 7, wherein the outer diameter of the wing plate is defined as a wing diameter, the wing plate has a first end surface, and the hydrodynamic pressure bearing can be installed in a shell cover , the shell cover has a second end face, the first end face and the second end face are located on the side of the wing plate and the shell cover that are far away from each other, the distance between the first end face and the second end face is defined as a fan height, the The height of the hydrodynamic bearing is defined as a bearing height, the inner diameter of the hydrodynamic bearing is defined as a bearing inner diameter, the bearing height is 0.6mm to 15mm, the bearing inner diameter is 0.6mm to 5mm, and the fan height is 1mm to 150mm, the size of the wing diameter is 1mm to 150mm. The combination of a hydrodynamic bearing and a wing plate as described in claim 8, wherein the inner diameter of the bearing is 0.6mm to 2mm, the height of the bearing is 0.6mm to 2mm, and the included angle of each oil guide groove is 10 degrees. to 40 degrees. The combination of a hydrodynamic bearing and a wing as described in claim 8, wherein the inner diameter of the bearing is 2 mm to 5 mm, the height of the bearing is 2 mm to 15 mm, and the included angle of each oil guide groove is 30 degrees to 90 degrees. Spend. The combination of a hydrodynamic bearing and a wing as claimed in claim 7, wherein the gap between the rotating shaft and the hydrodynamic bearing is 1 μm to 10 μm. The combination of a hydrodynamic bearing and a wing as described in claim 7, wherein the applicable temperature range of the hydrodynamic bearing is -40°C to 150°C, the lubricating fluid is an ester oil, or the hydrodynamic bearing The applicable temperature range of the hydrodynamic bearing is -50°C to 250°C, and the lubricating fluid is fluorine oil; or the applicable temperature range of the hydrodynamic bearing is -50°C to 160°C, and the lubricating fluid is silicone oil.

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